EP0442877A1 - Mecanisme de transmission a variation de vitesse - Google Patents

Mecanisme de transmission a variation de vitesse

Info

Publication number
EP0442877A1
EP0442877A1 EP89905136A EP89905136A EP0442877A1 EP 0442877 A1 EP0442877 A1 EP 0442877A1 EP 89905136 A EP89905136 A EP 89905136A EP 89905136 A EP89905136 A EP 89905136A EP 0442877 A1 EP0442877 A1 EP 0442877A1
Authority
EP
European Patent Office
Prior art keywords
journal
crank
shaft
con
rod
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP89905136A
Other languages
German (de)
English (en)
Inventor
Michael Joseph Egan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Barton Gordon Page
Original Assignee
Barton Gordon Page
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Barton Gordon Page filed Critical Barton Gordon Page
Publication of EP0442877A1 publication Critical patent/EP0442877A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/04—Crankshafts, eccentric-shafts; Cranks, eccentrics
    • F16C3/22—Cranks; Eccentrics
    • F16C3/28—Adjustable cranks or eccentrics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H29/00—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action
    • F16H29/02—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts
    • F16H29/04—Gearings for conveying rotary motion with intermittently-driving members, e.g. with freewheel action between one of the shafts and an oscillating or reciprocating intermediate member, not rotating with either of the shafts in which the transmission ratio is changed by adjustment of a crank, an eccentric, a wobble-plate, or a cam, on one of the shafts
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2142—Pitmans and connecting rods
    • Y10T74/2162—Engine type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins
    • Y10T74/2181—Variable

Definitions

  • This invention relates to variable ratio drive transmissions and in particular to variable throw crank drives for incorporation in such transmissions.
  • British Patent 132628 describes a variable stroke crank drive, comprising a crank shaft having a plurality of axially spaced big-end journals each having at least one connecting-rod (con-rod) mounted thereon through the intermediary of eccentric mounting means, the said means all being adjustable in unison to permit the eccentricity of each con-rod big-end to be adjusted from a minimum value to a maximum value, and a rotatable operating shaft extending axially through the crank shaft and operable, while the crank shaft is running, to vary the eccentrici ⁇ ties of the said eccentric mounting means in unison.
  • the drive disclosed does not, however, provide for preserving dynamic balance and would therefore be liable to substantial vibration at high operating speeds.
  • the present invention is mainly characterized in that the eccentric mounting means for each con-rod big-end comprises a journal mounted for radial displacement -. relative to the crank shaft, and that a corresponding counterweight is also mounted for radial displacement relative to the crankshaft, the journal and its counter ⁇ weight being radially displaceable in opposite directions by cam means fast with the operating shaft and operatively coupled to the said journal and its counterweight.
  • This arrangement provides for automatic counterbalancing of the shaft throughout the range of adjustment of the eccentricity of the eccentric mounting means.
  • the invention also provides a crank shaft, suitable for use in such a drive, fabricated from a plurality of components to facilitate its production.
  • Fig. 1 is a cross-section on the line YY of Fig. 2;
  • Fig. 2 is a longitudinal cross-section through the axis of the crank on the line XX in Fig. 1 ;
  • Fig. 2A is a scrap detail from Fig. 2, on a larger scale
  • Figs. 3A,3B; 4A,4B; 5A,5B; 6A,6B; 7A,7B; 8A,8B,8C; 9; 10A,10B; and 11A,11B,11C,11D, are sets of views of individual components of the drive transmis ⁇ sion. ;
  • Fig. 12 is an axial section on a drive shaft; and Fig. 13 is a scrap section showing an actuating means for the drive transmission.
  • the drive shown in the drawings is a continuously variable transmission for a tractor. It has a main crank axis CA and two parallel driven shafts DA 1 and DA 2. Each of these shafts carries three one-way clutches, in the form of sprag clutches whose outer races are all - connected to different respective con-rods each driving its associated sprag-clutch and drive shaft for up to 65° of arc whilst overriding the other two clutches on the same shaft.
  • the two drive shafts are coupled to a common output .
  • the con-rods all have adjustable throw, and means are provided for adjusting the throws of all six con-rods from zero to maximum value. At zero throw, no drive is transmitted to the driven shafts and at maximum throw, the shafts are driven at their maximum speed relative to the speed of rotation of the crank shaft.
  • Fig. 2 shows the length of the crank shaft on its axis CA.
  • the crank shaft is of fabricated construction, comprising a forward end main bearing and cam housing component 10, three journal housings 11, two middle sections 12 alternating axially with the housing 11, and a rear end main bearing and cam housing component 13. These components are rigidly secured together to form the crank shaft proper and as will be explained below, they provide "big-end" journal supports for three pairs of con-rods 14A,14B, three of which can be seen in Fig. 2 connected at their small ends to respective sprag- clutch outer races 16 on one draft shaft DA 1.
  • the main components of the crank shaft are illus ⁇ trated in Figs. 3A - 6B.
  • the component 10 has a journal section 101 and a main radial wall 102 terminating at rearwardly directed arcuate flanges 103 for bolting to the adjacent housing 11, illustrated in Figs. 4,4B.
  • the housing comprises a central, generally tubular body 111 having a radial peg 112 at its mid-length.
  • the side walls of the body 111 are given a slightly convex curved form to constitute guide surfaces 116.
  • the housing has two parallel, chordally directed legs 113 defining between them guide slots 114.
  • the legs 113 at one end of the first housing are bolted to the flanges 103 of the component 10, and those at the other end are bolted to the adjacent middle section 12, illustrated in Figs. 5A,5B.
  • This section comprises a tubular body 121 forming a jour ⁇ nal received in a fixed bearing, and at each end it has a - A -
  • radial plate 122 the two plates being mirror images of each, but set rigidly at 120° to each other.
  • the outer edges of both plates are formed with outwardly directed arcuate flanges 123 for securing the section to the legs 113 of the adjacent journal housings 11 to either side.
  • the next housing 11 will, of course be set at 120° to its predecessor, and with the interposition of the second, identical middle section 12 the third housing 11 will be a further 120° out of phase from its predecessor.
  • the rearmost limbs 113 of the third housing 11 are secured to the component 13 (Figs.
  • the big-end journals of the crank shaft are mounted in the journal housings 11 for sliding radial movement between a concentric position and a maximum eccentric position.
  • Figs. 7A,7B The detail of a big-end journal is illustrated in Figs. 7A,7B, wherein the journal 230 is seen to be com ⁇ posed of two parts 30A,30B dowelled and screwed together on assembly.
  • the journal has a large central aperture 31 and a radial extension thereof, 32, by which the journal engages over the central body 111 and the peg 112, respec ⁇ tively, the straight sides of the aperture 31 engaging slidingly against the guide surfaces 116.
  • This assembled condition is easily seen in Fig. 1, in which the journal is co-axially centred.
  • each journal housing also accommodates a pair of counterweights, of the form illustrated in Figs. 8A,8B,8C.
  • Each counterweight 36 is of generally C-shaped form, having an elongate slot 37 formed in a central web portion 38 of reduced thickness also adapted to slide over the faces 116 of housing body 111.
  • the weights each have an axially directed drive pin 39 for co-operation with oper ⁇ ating cams.
  • each housing 11 accommodates between its respective ends, a big-end journal 30, flanked on either side by a counterweight 36.
  • the respective projecting pins 33 and 39 project axially through the slots 114 at both ends of the housing 11 , and are guided for radial sliding movement therein by bronze sliding bushes.
  • Each cam 40 is of generally plate like form and has a central through hole 41 of splined form. It also has two curved cam slots 42,43 of similar but mirror image profile. In the assembled drive, one slot 42 will receive and guide one of the pins 33 of one journal and one slot 43 will receive the pin 39 of a counterweight 36.
  • cams 40 in the illustrated drive arranged in pairs, one immediately adjacent the axial side faces of each of the journal housings 11, as best seen in Fig. 2, which also shows the central operating shaft 45 extending along the main axis CA and having splined, driving connections to each of the six cams.
  • each big-end journal 30 carries two con-rods 14A,14B the construction of which is shown in detail in Figs. 10A,10B,11A,11B,11C and 11D. Figs.
  • 10A and 10B illustrate the form of an inner con-rod 14A of generally conventional form having a cylin ⁇ drical bearing portion 141 , a radial rod 142 and a small end bearing 143.
  • the outer con-rod 14B has a cylindrical bearing portion 144 formed with inwardly directed radial flanges 146 forming an enclosure to receive and capture the bearing portion 141 of the inner con-rod which thus forms a journal for the outer . con-rod.
  • the side wall of the portion 144 is interrupted to form a slot 147 of some 94° of arc through which the rod 142 emerges, in the same plane as the rod 1 8 of the outer con-rod, terminating at small end bearing 149.
  • Fig. 12 is a sectional elevation on one of the two drive shafts DA 1 ,DA 2, which are identical in con ⁇ struction and comprise in each case a drive shaft 150 shown here as constructed in sections for manufacturing convenience but effectively forming a solid shaft.
  • Three sprag clutches are built onto the shaft, each sprag clutch having an outer race 16 supported on the shaft 150 by a pair of ball (or roller) bearings 152.
  • the portion of shaft 150 between each pair of bearings constitutes the inner race 153 of a sprag clutch the sprag elements of which are indicated at 154.
  • Each of the outer races has an offset, axially projecting pin 156 which is received in the small end bearing 143 or 149 of a respective con-rod.
  • the shaft is supported at intervals by rotary bearings 157 and it carries at one end an output drive gear 158.
  • the two shafts DA 1 ,DA 2 are arranged in parallel with each other and their drive gears 158 are both engaged with a common output gear.
  • the crank shaft is coupled to a prime mover, such as the flywheel of an i.e. engine.
  • a prime mover such as the flywheel of an i.e. engine.
  • the crank shaft rotates but no motion is imparted to the other con-rods and drive shafts 150 (DA 1 ,DA 2).
  • the control shaft 45 is displaced angularly relative to the crank shaft, both of course continuing to rotate at engine speed.
  • Angular displacement of the shaft 45 correspondingly rotates the cams 40, causing each of the journals 30 to be displaced radially away from its neutral, concentric position.
  • the counterweights 36 are displaced in the the opposite radial direction to maintain dynamic balance.
  • the con-rods 14A and 14B will be corre ⁇ spondingly reciprocated, to effect in turn angular oscil ⁇ lation of the sprag clutch races 16.
  • the amplitude of oscillation of the races 16 may be from 0° to. approximate ⁇ ly 65°. Because the pair of con-rods on each journal are angularly offset by 60°, they will operate in sequence upon their respective sprag races on the two shafts 150 and because the three journal housings 11 are offset 120° from each other, the three con-rods 14A will operate 120° out of phase with each other, as will the three con-rods 14B.
  • each of the sprag races 16 will be driven through '65° in one revolution of the crank shaft, the races on each shaft
  • the two shafts 150 are also driven 60° out of phase with each other so that all six sprag clutches contribute about 60° of drive in each revolution of the crank shaft, about 180° of revolution being contributed by each drive shaft to the final drive output, which accordingly rotates through about 360° for one revolution of the crank shaft.
  • each sprag clutch outer body is driven through 65° in each revolution of the crank, there is a ransmission loss within the clutch of about 10° so that each shaft 150 is positively driven through rather less than 180°, resulting in a maximum drive ratio of less than 1:1.
  • Angular adjustment of the control shaft 45 might be effected in various ways but a presently preferred arrangement is illustrated in Fig. 13, which is a scrap- section on the main axis CA, to the right of the drive as seen in Fig. 2 and on a larger scale.
  • the extreme right hand end of the control shaft 45 is screw-threadedly secured to the end of the inner race 160 of a ball nut and screw having bearing balls 161 and an outer race 162 secured in a support cup 163 arranged in telescopic sliding relationship to the extreme rear end of the rear bearing and housing component 13.
  • the support cup 163 is engaged through thrust races 164 with an internal flange 165 of an actuator 166 which is threaded into a rotary support cup 167 which is rotatable in the main housing and relative to the crank shaft and components fast therewith.
  • the actuator 166 is keyed to the housing at 168 so as to be fast against rotation, but displaceable axially.
  • Rotation of the cup 167 may be effected in many ways, in response to manual control or automatically in response to demand from the prime mover or driven equipment.
  • variable throw crank may be incorporated directly in the engine, replacing the usual crank shaft so as to permit direct adjustment of the piston stroke, and thus the compression ratio, of the engine.
  • the particular crank configuration illustrated herein would lend itself particularly well to incorporation in a V-6 diesel engine, for example.
  • the ability to adjust the piston stroke is particularly useful since diesel engines typically require a relatively high compression ratio for starting purposes, a medium compression ratio when under moderate load and a low ratio under full load. Only very small adjustments in stroke are required to effect these variations in compression ratio.
  • Many different applications of the invention will also be possible, as well as modifications to the particular construction described above. For example, other forms of one-way clutch can be employed in place of sprag clutches.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • Transmission Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

Mécanisme de transmission à variation continue, où tourillons (30) et contrepoids (36) se déplacent simultanément dans des directions radiales opposées au moyen d'un mécanisme à cames (40) monté sur un arbre rotatif d'entraînement (45).
EP89905136A 1988-11-08 1989-05-04 Mecanisme de transmission a variation de vitesse Withdrawn EP0442877A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB888826112A GB8826112D0 (en) 1988-11-08 1988-11-08 Variable ratio drive transmission
GB8826112 1988-11-08

Publications (1)

Publication Number Publication Date
EP0442877A1 true EP0442877A1 (fr) 1991-08-28

Family

ID=10646481

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89905136A Withdrawn EP0442877A1 (fr) 1988-11-08 1989-05-04 Mecanisme de transmission a variation de vitesse

Country Status (6)

Country Link
US (1) US5189927A (fr)
EP (1) EP0442877A1 (fr)
JP (1) JPH04501452A (fr)
AU (1) AU639205B2 (fr)
GB (1) GB8826112D0 (fr)
WO (1) WO1990005252A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4201095A1 (de) * 1992-01-17 1993-07-22 Raster Maschinen Gmbh Synchron verstellbarer dynamischer massenausgleich an exzenterpressen oder -stanzen mit automatischer hubverstellung
US20040083836A1 (en) * 2002-11-06 2004-05-06 Transvantage, L.L.C. Continuously variable mechanical transmission
US6938589B2 (en) 2002-11-07 2005-09-06 Powervantage Engines, Inc. Variable displacement engine
ITTV20050018A1 (it) * 2005-02-03 2006-08-04 Adriano Girotto Trasmissione a rapporto di trasmissione variabile linearmente.
CN102027267B (zh) * 2008-04-15 2014-07-09 舍弗勒技术股份两合公司 用于调节用于曲柄-cvt变速器的偏心量的装置
WO2010009698A1 (fr) * 2008-07-21 2010-01-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Dispositif d’entraînement pour une transmission à variation continue d’un véhicule à moteur
JP5570512B2 (ja) * 2008-10-16 2014-08-13 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 自動車の伝動装置のための駆動軸アッセンブリ
JP5095581B2 (ja) * 2008-11-05 2012-12-12 本田技研工業株式会社 歩行補助装置
CN103649594B (zh) * 2011-07-13 2016-03-09 本田技研工业株式会社 无级变速器
CN104797859B (zh) * 2012-11-29 2017-04-26 本田技研工业株式会社 车辆用动力传递装置
BR112015012263A2 (pt) * 2012-12-05 2017-07-11 Honda Motor Co Ltd dispositivo de transmissão de potência do veículo
WO2015104805A1 (fr) * 2014-01-08 2015-07-16 本田技研工業株式会社 Dispositif de transmission de puissance de véhicule
CN106089422B (zh) * 2016-08-22 2018-07-03 上海毓迪动力科技有限公司 带有多个平衡轴的热力学单缸发动机

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB132628A (fr) * 1900-01-01
US1924562A (en) * 1927-05-14 1933-08-29 Nathan M Lower Bearing mounting for crank shafts and the like
US1986549A (en) * 1928-10-01 1935-01-01 Packard Motor Car Co Internal combustion engine
US1875180A (en) * 1930-07-08 1932-08-30 Utah Royalty Corp Means for converting motion and the like
US2204514A (en) * 1937-06-03 1940-06-11 Automatic Power Transmission C Transmission
FR843452A (fr) * 1937-09-28 1939-07-04 Perfectionnements aux arbres dits vilebrequins
FR857205A (fr) * 1939-07-03 1940-08-31 Mécanisme de transmission de force à vitesse variable
US3985114A (en) * 1975-05-19 1976-10-12 Alto Automotive, Inc. Apparatus for shock mounting of piston rods in internal combustion engines and the like
US4085628A (en) * 1976-06-07 1978-04-25 Mcwhorter Edward Milton Intra-articulate reciprocating engine system
US4319498A (en) * 1979-06-11 1982-03-16 Mcwhorter Edward M Reciprocating engine
IN155023B (fr) * 1980-01-02 1984-12-22 Nat Res Dev
US4467756A (en) * 1980-02-11 1984-08-28 Mcwhorter Edward M Partially constrained five-bar mechanism for reciprocating piston engines
US4622864A (en) * 1985-06-03 1986-11-18 General Motors Corp. Modular crank subassembly and built-up crankshaft therefor

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9005252A1 *

Also Published As

Publication number Publication date
JPH04501452A (ja) 1992-03-12
GB8826112D0 (en) 1988-12-14
AU639205B2 (en) 1993-07-22
WO1990005252A1 (fr) 1990-05-17
US5189927A (en) 1993-03-02
AU3542889A (en) 1990-05-28

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